JP2001138894A - High pressure fluid feeding apparatus and hydraulic brake device for vehicle provided with the apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a high pressure fluid feeding apparatus and a hydraulic brake device for vehicle provided with the above apparatus capable of inhibiting a noise and a vibration generated when high pressure fluid from a high pressure generation source is fed to a pressure-forming chamber. SOLUTION: This hydraulic brake device is provided with a spool cylinder 34 and a spool valve 35 slidably supported in a hollow portion of the cylinder 34. A first communication hole 70 for introducing high pressure brake fluid to the hollow portion is provided on the cylinder 34 and a first circumferential groove 77 is provided on a valve 35. A flow passage communicating with a control chamber R4 is formed between the cylinder 34 and the first circumferential groove 77. When the valve 35 slides in the cylinder 34, the high pressure brake fluid is fed to the control chamber R4 through a flow passage, etc., formed between the cylinder 34 and the first circumferential groove 77. A stepped portion of the first circumferential groove 77 is gently formed through an inclined surface 80a.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a high-pressure fluid supply device for supplying a high-pressure fluid from a high-pressure source to a pressure forming chamber, and a hydraulic brake device for a vehicle equipped with the high-pressure fluid supply device.

[0002]

2. Description of the Related Art Conventionally, as a high-pressure fluid supply device for supplying a high-pressure fluid from a high-pressure source to a pressure forming chamber, for example, those shown in FIGS. 10 and 11 are known. As shown in FIG.
And a shaft 1 slidably supported in a hollow portion of the cylindrical body 101
02.

A communication hole 103 for introducing a high-pressure fluid from a high-pressure source into a hollow portion thereof is formed in the cylindrical body 101 so as to penetrate in a radial direction. The shaft 102
Is provided with a concave portion 104. A flow path communicating with the pressure forming chamber 105 is formed between the cylindrical body 101 and the recess 104.

In this high-pressure fluid supply device, when the relative position between the cylinder 101 and the shaft 102 is in the state shown in FIG. 10, the opening of the communication hole 103 and the recess 104 are separated from each other. The opening of the communication hole 103 is closed by the outer peripheral surface of the shaft body 102, and the high-pressure fluid from the high-pressure generation source is not supplied to the pressure forming chamber 105 from the communication hole 103.

On the other hand, the shaft 102 slides inside the cylinder 101, and the relative positions of the cylinder 101 and the shaft 102 are shown in FIG.
In the state described above, the opening of the communication hole 103 opens in the recess of the shaft 102, and the high-pressure fluid from the high-pressure generation source passes through the passage formed between the communication hole 103, the cylinder 101, and the recess 104. The pressure is supplied to the pressure forming chamber 105 via the pressure generating chamber 105.

[0006]

In this high-pressure fluid supply device, the shaft 104 is formed by the recess 104.
The step portion 104a formed on the outer peripheral surface of the second 2 is formed in a substantially step shape. Therefore, the high pressure source (communication hole 10
When the high-pressure fluid from 3) is introduced into the flow path formed between the cylindrical body 101 and the concave portion 104 and supplied to the pressure-forming chamber 105, the high-pressure fluid generates cavitation, for example, causing significant noise and noise. Vibration may occur.

An object of the present invention is to provide a high-pressure fluid supply device and a high-pressure fluid supply device capable of suppressing noise and vibration generated when a high-pressure fluid from a high-pressure source is supplied to a pressure forming chamber. An object of the present invention is to provide a hydraulic brake device for a vehicle.

[0008]

In order to solve the above-mentioned problems, the present invention according to claim 1 comprises a cylinder having a communication hole for introducing a high-pressure fluid from a high-pressure source into a hollow portion; A shaft body slidably supported in a hollow portion of the cylinder body and having a recess formed on an outer peripheral surface forming a flow path communicating with the pressure forming chamber between the cylinder body and the cylinder body; In a high-pressure fluid supply device for relatively moving a shaft to open the communication hole to the recess and supplying high-pressure fluid from a high-pressure source to a pressure forming chamber, the high-pressure fluid supply device is formed on the outer peripheral surface of the shaft by the recess. The step is
The gist of the present invention is that it is formed gently via an inclined surface.

According to a second aspect of the present invention, in the high-pressure fluid supply device according to the first aspect, the recess is provided around the shaft. According to a third aspect of the present invention, in the high-pressure fluid supply device according to the first or second aspect, the recess is configured to reduce a flow path communicating with a pressure forming chamber formed between the cylindrical body. The gist is that a projecting portion projecting toward the shaft body is formed.

According to a fourth aspect of the present invention, in the high-pressure fluid supply device according to the third aspect, the step formed on at least one of the upstream side and the downstream side of the protruding portion is provided with an inclined surface. The point is that it is formed smoothly.

According to a fifth aspect of the present invention, there is provided a hydraulic brake device for a vehicle including the high-pressure fluid supply device according to any one of the first to fourth aspects. (Operation) According to the configuration of the first aspect of the invention, the step formed on the outer peripheral surface of the shaft body by the concave portion is smoothly formed via the inclined surface. Therefore, the high-pressure fluid from the high-pressure source (communication hole) does not generate cavitation, for example, and the high-pressure fluid is smoothly introduced into the flow path formed between the cylinder and the concave portion, and is introduced into the pressure forming chamber. Supplied. For this reason, generation of noise and vibration when the high-pressure fluid from the high-pressure generation source (communication hole) is supplied to the pressure forming chamber is suppressed.

According to the second aspect of the present invention, the concave portion is provided around the shaft. Therefore, the flow path formed between the cylinder and the concave portion is maximized, and the high-pressure fluid is quickly supplied to the pressure forming chamber.

Further, such a concave portion is easily processed by, for example, a lathe operation. According to the configuration of the third aspect of the present invention, the concave portion is formed with a projecting portion for narrowing a flow path communicating with the pressure forming chamber formed between the cylindrical portion and the cylindrical body. Therefore, the pressure difference between the high pressure fluid flowing into the pressure forming chamber and the high pressure fluid is reduced, and the generation of noise and vibration is further suppressed.

According to the fourth aspect of the present invention, the step formed on at least one of the upstream side and the downstream side of the protruding portion is formed gently via the inclined surface. Therefore, the high-pressure fluid introduced into the flow path formed between the cylindrical body and the concave portion is smoothly throttled, or the throttled high-pressure fluid smoothly flows into the pressure forming chamber.

According to the fifth aspect of the present invention, these high-pressure fluid supply devices are provided in a hydraulic brake device of a vehicle. Generally, the hydraulic brake device is mounted immediately in front of a brake pedal arranged in a driver's seat. Therefore, since the generation of noise and vibration due to cavitation of the high-pressure fluid is suppressed, the generation of unpleasant noise and the like transmitted to the driver is also reduced.

[0016]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A hydraulic brake device for a vehicle to which one embodiment of the present invention is applied will be described below with reference to FIGS.

FIG. 1 is a sectional view showing the hydraulic brake device. As shown in FIG. 1, the hydraulic brake device generates a required hydraulic pressure by a push rod 11 connected to a brake pedal 10 and a movement of the push rod 11 in accordance with the operation of the brake pedal 10. A hydraulic pressure control cylinder 12, a brake fluid reservoir 13 in which brake fluid is stored, an auxiliary hydraulic pressure source 14 as a high-pressure generating source for generating a high-pressure (power hydraulic) brake fluid as a high-pressure fluid; Wheel cylinders 17 and 18 are provided on the front wheel 15 and each rear wheel 16 (only one is shown in FIG. 1).

A cylinder body 21 forming the outer shape of the hydraulic control cylinder 12 penetrates along its axis, and corresponds from one side (right side in FIG. 1) corresponding to the rear side of the vehicle to the front side. To the other side (left side in FIG. 1),
A first hole 21a, a second hole 21b smaller in diameter than the first hole 21a, and a third hole 2 smaller in diameter than the second hole 21b
1c and a stepped fourth hole 21d are formed.
In the cylinder body 21, a hydraulic passage 22 communicating the rear part of the second hole 21b and the fourth hole 21d, a front part of the second hole 21b, and the brake fluid reservoir 13 are provided on the upper side of FIG. The hydraulic pressure path 23 which communicates with the hydraulic pressure path 2 which communicates the substantially middle portion of the fourth hole 21d with the brake fluid reservoir 13.
1, a hydraulic passage 25 communicating the rear of the second hole 21b with the wheel cylinder 18, a hydraulic passage 26 communicating the rear of the third hole 21c with the wheel cylinder 17, A hydraulic path 27 communicating between the front part and the rear part of the fourth hole 21d, and a hydraulic path 28 communicating a substantially middle part of the fourth hole 21d and the auxiliary hydraulic pressure source 14 are formed. In addition, as shown in FIG.
The spaces 5 are communicated with each other by a peripheral groove 29 formed in the second hole 21b corresponding to the opening. As shown in FIG. 3, the hydraulic passages 22 and 27 communicate with each other by a circumferential groove 30 formed in the fourth hole 21d corresponding to the opening.

The hydraulic pressure control cylinder 12 includes a master piston 31, a valve body 32, and a control piston 3 accommodated in the first to fourth holes 21a to 21d of the cylinder body 21.
3, a spool cylinder 34 as a cylinder, a spool valve 35 as a shaft, a plunger 36, a sleeve 37,
A reaction force rod 38, a reaction force disc 39 and a plug 40 are provided.

The master piston 31 has a first piston 41 and a second piston 42. As shown in FIG. 2, the first piston 41 is connected to the second hole 21.
b having a slightly smaller outer diameter than the inner diameter of the second hole 21.
b, and a cylindrical portion 44 having a diameter smaller than that of the disk portion 43 and projecting toward the first hole 21a. The first piston 41 is provided between the first hole 21a and the cylindrical portion 44 and has a substantially cylindrical sleeve 45 provided with a seal member. The first piston 41 is provided between the second hole 21b and the disk portion 43. The first and second holes 21a and 21b are slidably supported in a liquid-tight manner by the annular seal member 43a. The inner peripheral surface of the first hole 21a, the boundary surface between the first and second holes 21a and 21b,
A space formed by the outer peripheral surface and the boundary surface of the cylindrical member 3 and the cylindrical portion 44, the front end surface of the sleeve 45, and the like is a power chamber R1. The power chamber R1 is connected to the peripheral groove 29 (the hydraulic passages 22, 25) via a clearance C1 formed between the inner peripheral surface of the second hole 21b and the outer peripheral surface of the disk portion 43.
Is in communication with

A transmission member 46 connected to the end of the push rod 11 inserted into the cylindrical portion 44 is mounted inside the cylindrical portion 44. This transmission member 46
The bolt 46a is fastened to a contact member 47 that penetrates the disk 43 along the axis at the bolt portion 46a and protrudes toward the second piston 42. Accordingly, the first piston 41, the transmission member 46, and the contact member 47 are integrally connected, and as shown in FIG. 2, when the push rod 11 moves forward based on the operation of the brake pedal 10, it is integrated. Move. Since the volume of the power chamber R1 is expanded as the first piston 41 advances, more brake fluid flows into the power chamber R1.

The second piston 42 is accommodated on the front side (left side in FIG. 1) of the first piston 41 (disk portion 43) with a slight gap. As shown in FIG. 2, the second piston 42 is formed in a substantially cylindrical body, and has an outer diameter slightly smaller than the inner diameter of the second hole 21b and the third hole 21c at the rear and front portions. Have the second
A first flange 42a and a second flange 42b are respectively formed at the rear portions of the third holes 21b and 21c. The second piston 42 is slidably supported by the first and second flanges 42a and 42b with respect to the second and third holes 21b and 21c, respectively.

A recess 48 is formed at the rear of the second piston 42 so as to face the contact member 47 and to contact the contact member 47. Therefore, as shown in FIG. 2, when the first piston 41 (push rod 11) moves forward, the second piston 42 is pressed by the contact member 47 in the concave portion 48 and moves.

Further, a substantially cylindrical valve body supporting portion 52 whose diameter is reduced through a step portion 51 is formed to extend in front of the second piston 42. The valve body 32 is accommodated in the valve body support portion 52.

Here, the first and second flanges 42 are used.
a and 42b between the inner peripheral surface of the second hole 21b and the second hole 21b.
The space formed by the outer peripheral surface of the piston 42 is a liquid supply chamber R2. The liquid supply chamber R2 is provided with the disk portion 43.
The power chamber R is provided by a seal member 43a attached to the power chamber R.
1 and separated. Further, the liquid supply chamber R2 communicates with the brake fluid reservoir 13 via the hydraulic path 23. As shown in FIG. 2, the second piston 42 has a through hole 53 penetrating in a meridian direction corresponding to the liquid supply chamber R2, and a valve body supporting portion 52 penetrating in the axial direction. A communication passage 54 communicating with the through hole 53 is formed. Therefore, the hollow portion of the valve body support portion 52 communicates with the liquid supply chamber R2 through the communication passage 54 and the through hole 53.

The second piston 42 is provided with an annular cup-shaped sealing member 55 that is folded forward at the step 51. This sealing member 55
The brake fluid in the supply chamber R2 is filled with the third hole 21c.
Through the clearance C2 formed between the inner peripheral surface of the second flange 42b and the outer peripheral surface of the second flange 42b, and allows the brake fluid at the front to flow into the same through the clearance C2. It has a function as a check valve for inhibiting the inflow into the chamber R2.

The valve element 32 is housed in the valve element support section 52 and is locked by a retainer 56 fitted on the outer peripheral portion of the valve element support section 52. An elastic body made of rubber, for example, is attached to the rear end of the valve body 32.
When the second member 2 comes into contact with the second piston 42 (the opening of the communication passage 54), the hollow portion of the valve body supporting portion 52 and the communication passage 54 are shut off. Therefore, when the second piston 42 moves forward and is pressed by the valve body 32, the communication between the liquid supply chamber R <b> 2 and the hollow portion of the valve body support 52 is interrupted by the valve body 32.

A rod 5 is provided at the front end of the valve body 32.
7 are integrally formed, and as shown in FIG. 3, a locking portion 57a is formed at the distal end thereof. The control piston 33 is accommodated in the third hole 21c in front of the master piston 31. As shown in FIG. 3, a third portion having an outer diameter slightly smaller than the inner diameter of the third hole 21c is provided at a substantially intermediate portion of the control piston 33.
A flange 58 is formed, a first cylindrical portion 59 having an outer diameter slightly smaller than the inner diameter of the third hole 21c at the front portion of the control piston 33, and an inner diameter at the front side of the first cylindrical portion 59. The enlarged second cylindrical portions 60 are formed. The control piston 33 is slidably fitted to the third hole 21c by the third flange 58 and the first and second cylindrical portions 59 and 60, and is mounted on the outer peripheral surface of the first cylindrical portion 59. It is liquid-tightly supported by the annular seal member 59a. Incidentally, the third flange 58 communicates in the axial direction.

Here, a space formed between the master piston 31 (second piston 42) and the control piston 33 in the third hole 21c is a pressure chamber R3. The pressure chamber R3 is substantially separated from the liquid supply chamber R2 by a seal member 55 mounted on the second piston 42.

As shown in FIG. 3, the control piston 33 has a through hole extending in the axial direction and opening at the rear end, and penetrating radially between the third flange 58 and the first cylindrical portion 59. 61 are formed. The through hole 61 accommodates the locking portion 57a of the valve body 32. The locking portion 57a is locked to a retainer 62 fitted to a rear portion of the control piston 33.

The retainer 56 fitted to the valve body support 52 of the second piston 42 and the control piston 3
A spring 63 is interposed between the retainer 62 and the retainer 62 fitted to the rear portion of the spring 3. Therefore, as shown in FIG. 3, when the master piston 31 (the second piston 42) advances, the control piston 33 advances integrally via the spring 63.

A locking pin 64 protruding in the radial direction is fixed to the cylinder body 21 behind the first cylindrical portion 59. Therefore, the movement range of the control piston 33 is restricted between the third flange 58 and the first cylindrical portion 59.

Here, the hydraulic path 26 is opened in the third hole 21c corresponding to the position of the locking pin 64. Therefore, the pressure chamber R3 and the wheel cylinder 17 communicate with each other through the hydraulic path 26.

The spool cylinder 34 is fitted on the front side of the control piston 33 in the fourth hole 21d. The spool cylinder 34 is provided with the third hole 2
The control piston 33 is formed in a substantially cylindrical shape with an outer diameter slightly smaller than the inner diameter and an inner diameter slightly smaller than the inner diameter of the first cylindrical portion 59 of the control piston 33. An annular first sealing member 34a, a second sealing member 34b, and a third sealing member 34c are mounted on the outer peripheral surface of the spool cylinder 34, and are fixed to the fourth hole 21d in a liquid-tight manner. I have.

At the rear end of the spool cylinder 34, there is formed a cylindrical portion 65 whose outer peripheral surface is reduced in diameter and protrudes. As shown in FIG. 4, a peripheral groove 66 is formed on the inner peripheral surface in front of the base end of the cylindrical portion 65. On the other hand, at the front end of the spool cylinder 34, a cylindrical portion 67 protruding forward is formed. A through hole 68 is formed in the cylindrical portion 67 so as to penetrate in the radial direction corresponding to the opening of the hydraulic path 24. This through hole 68
Communicates with the circumferential groove 69 formed in the fourth hole 21d corresponding to the opening of the hydraulic passage 24. Therefore, the hollow portion of the cylindrical portion 67 is provided with the through hole 68, the circumferential groove 69, and Hydraulic passage 2
4 communicates with the brake fluid reservoir 13.

The first and second sealing members 3
4a, 34b, the second and third sealing members 34
A first communication hole 70 and a second communication hole 71 as communication holes penetrating in the radial direction are formed between b and 34c, respectively. The spool cylinder 34 has a third communication hole 72 that extends in the axial direction and has one end connected to the second communication hole 71 and the other end opened to the third hole 21c. The first communication hole 70 is formed in the circumferential groove 7 formed in the fourth hole 21d corresponding to the opening of the hydraulic passage 28.
3 and thus communicates with the auxiliary hydraulic pressure source 14 through the circumferential groove 73 and the hydraulic pressure passage 28.

The spool valve 35 has a rear portion and a front portion each having a first cylindrical portion 59 of the control piston 33.
Has an outer diameter slightly smaller than the inner diameter of the spool cylinder 34 and an outer diameter slightly smaller than the inner diameter of the spool cylinder 34. The rear part of the spool valve 35 is mounted in a liquid-tight manner with respect to the first cylindrical part 59,
Locked to the control piston 33. More specifically, a retainer 74 is fitted on the inner wall surface of the first cylindrical portion 59, and a spring 75 is interposed between the retainer 74 and the spool cylinder. The spool valve 35 is biased by the spring 75 so as to contact the control piston 33. The front part of the spool valve 35 is slidably supported on the spool cylinder 34.

Here, the fourth hole 21d, the inner wall surface of the second cylindrical portion 60 of the control piston 33, the spool cylinder 34
A space formed by the rear end face, the outer peripheral face of the spool valve 35, and the like is a control chamber R4 as a pressure forming chamber. The control chamber R4 is separated from the pressure chamber R3 by a seal member 59a mounted on the control piston 33. The control chamber R4 is provided with the hydraulic passage 27.
Corresponding to the opening, and communicates with the hydraulic path 27 through a peripheral groove 76 formed in the fourth hole 21d.

As shown in FIGS. 4 and 5, the spool valve 35 faces the circumferential groove 66 of the spool cylinder 34 in the initial state (return state) of the control piston 33 (brake pedal 10). A first circumferential groove 77 forming a concave portion is formed on the outer peripheral surface. The first circumferential groove 77 is provided on the outer peripheral surface of the spool valve 35.
A second peripheral groove 78 that forms a concave portion is formed at a predetermined interval axially rearward of the groove. The first bank 79 and the second bank 80 as the projecting portions are provided on the rear side and the front side of the first circumferential groove 77, respectively. In the present embodiment, the first bank 79
As shown in FIG. 5, the step portions formed at the rear and front portions of the rear surface have inclined surfaces 79 that are substantially linear in cross section.
a, 79b are formed smoothly. Also,
The step formed at the rear of the second bank 80 is also formed gently via an inclined surface 80a that is substantially linear in cross section.

As shown in FIG. 5, in the initial state of the control piston 33 (spool valve 35), the inner peripheral surface of the spool cylinder 34 and the spool valve 35
Although there is a slight clearance C3 between the outer peripheral surfaces of the (first and second banks 79, 80), the opening of the first communication hole 70 is closed by the spool valve 35, and the first communication hole 70 is closed. The space between the hole 70 and the control room R4 is substantially shut off. Therefore, the auxiliary hydraulic pressure source 14 communicating with the first communication hole 70 through the circumferential groove 73 and the hydraulic pressure passage 28 is connected to the control chamber R
4 and cut off. The opening of the second communication hole 71 is not closed by the spool valve 35, and the hollow portion of the spool cylinder 34 and the control chamber R4 are connected via the second and third communication holes 71 and 72. Communicating. Therefore, the brake fluid reservoir 13 and the control chamber R4 communicate with each other through the fluid pressure passage 24, the circumferential groove 69, the through hole 68, and the second and third communication holes 71 and 72. Thus, the control chamber R4 is filled with the brake fluid at atmospheric pressure.

On the other hand, as shown in FIGS. 6 and 7, when the control piston 33 (spool valve 35) advances, the first communication hole 70 opens in the first circumferential groove 77 and the control piston 33 (spool valve 35) opens. The peripheral groove 66 and a part of the second peripheral groove 78 overlap, and the first communication hole 70 and the control room R4 are in the first
A communication passage formed between the communication hole 70 and the first peripheral groove 77;
The communication is made through a communication passage formed between the peripheral groove 66 and the first peripheral groove 77 and a communication passage formed between the peripheral groove 66 and the first bank 79. Therefore, the auxiliary hydraulic pressure source 14 and the control room R
4 is communicated through the hydraulic passage 28, the peripheral groove 73, the first communication hole 70, the peripheral groove 66, the first peripheral groove 77, and the like. At this time,
Since the second bank 80 is formed with the inclined surface 80a, the high-pressure (power hydraulic) brake fluid from the auxiliary hydraulic pressure source 14 (the first communication hole 70) does not undergo cavitation, for example. The brake fluid smoothly flows through the first circumferential groove 7
Flow into the 7 side. The high-pressure brake fluid that has flowed into the first circumferential groove 77 is again narrowed in the communication path formed between the circumferential groove 66 and the first bank 79, and then flows into the second circumferential groove 77. It flows into the 78 side. As described above, the high-pressure brake fluid from the auxiliary hydraulic pressure source 14 is supplied to the control chamber R4. Since the opening of the second communication hole 71 is closed by the spool valve 35 (second bank 80), the control chamber R4 communicating with the second communication hole 71 and the third communication hole 72 is It is shut off from the brake fluid reservoir 13.

The plunger 36 is fitted to the front of the spool valve 35. As shown in FIG. 4, a contact portion 36a formed at the front end of the plunger 36 is axially forward of the spool valve 35. It protrudes.

The sleeve 37 is provided on the spool cylinder 3
4, the rear and front portions have outer diameters slightly smaller than the inner diameter of the cylindrical portion 67 of the spool cylinder 34 and the inner diameter of the fourth hole 21d, respectively. The sleeve 37 has a rear portion formed of the cylindrical portion 6.
7 so as to be accommodated in the fourth hole 21d. In addition, two seal members 81 and 82 are mounted on the outer peripheral surface of the sleeve 37 that is in contact with the fourth hole 21d at predetermined intervals in the axial direction. Further, the hollow portion of the sleeve 37 is enlarged in diameter at the front, and the rear portion and the front portion have the rod accommodating portion 83 and the disc accommodating portion
It is 4.

The reaction force rod 38 is accommodated in the rod accommodating portion 83 so as to be slidable in the axial direction. The rear end of the reaction force rod 38 is opposed to the contact portion 36 a of the plunger 36.

The disk accommodating portion 84 is mounted with a reaction disk 39 made of rubber, for example. The reaction rod 38 is moved forward in the axial direction when its front end comes into contact with the reaction disk 39. Movement is regulated. Further, the plug 40 is fitted to the front side of the disk accommodating portion 84 with respect to the reaction disk 39. Then, as shown in FIG.
The spring 85 interposed between the reaction force disc 39 and the plug 40 presses the reaction force rod 38 toward the reaction force rod 38.

The space defined by the opposing surface of the fourth hole 21d, the reaction disk 39 and the plug 40 is a reaction chamber R5. The reaction force chamber R5 is formed in a liquid-tight manner by a seal member 86 and a reaction force disk 39 mounted on the outer peripheral surface of the plug 40.

At substantially the middle portions of the seal members 81 and 82 corresponding to the reaction force chamber R5 of the sleeve 37, there are formed through holes 87 and 88 penetrating in the radial direction on the upper and lower sides in FIG. . These through holes 87 and 88 are respectively connected to the hydraulic passages 22 and 27 and the reaction force chamber R through the circumferential groove 30.
5 is communicated. Therefore, the control room R4 and the reaction force room R5
Are the circumferential groove 76, the hydraulic path 27, the circumferential groove 30, and the through hole 88.
The reaction chamber R5 and the power chamber R1 communicate with each other through the through-hole 87, the circumferential groove 30, the hydraulic path 22, the circumferential groove 29, and the clearance C1, and the power chamber R1
And the wheel cylinder 18 have a clearance C1,
It communicates via the circumferential groove 29 and the hydraulic path 25.

As shown in FIG. 8, when the hydraulic pressure in the reaction force chamber R5 is small, the spool valve 3
5 (plunger 36) moves forward without being restricted by the reaction force rod 38, but when the hydraulic pressure in the reaction force chamber R5 becomes larger than a predetermined pressure, the reaction force disc 39 as shown in FIG. Is elastically deformed to be swelled into the rod accommodating portion 83 by being pressed by the liquid pressure. At this time, the bulging portion of the reaction force disc 39 comes into contact with the front end of the reaction force rod 38, and the reaction force rod 38 is pushed rearward on the plunger 36 side. When the rear end of the reaction force rod 38 is pressed by the contact portion 36a of the plunger 36, the spool valve 35 (control piston 33) is pushed back.

The auxiliary hydraulic pressure source 14 is for generating a high pressure (power hydraulic pressure) in the brake fluid, and includes an accumulator 91, a hydraulic pump 92, and an electric motor 93. The auxiliary hydraulic pressure source 14 is connected to the electric motor 9.
3 drives the hydraulic pump 92 to suck and pressurize the brake fluid in the brake fluid reservoir 13 and discharge it to the accumulator 91. The accumulator 91 communicates with the hydraulic passage 28, and therefore, the first communication hole 70
When the control room R4 communicates with the control room R4,
Supply high pressure brake fluid to

Next, the operation of the hydraulic brake device will be described. As shown in FIG. 1, the brake pedal 1
In the initial state (return state) in which the second piston 42 is not pressed by the valve body 32, the pressure chamber R3 (the hollow portion of the valve body support portion 52) and the communication passage 54 are not pressed. Is in communication with Therefore, the brake fluid reservoir 13 and the pressure chamber R3 are connected to the hydraulic pressure passage 23 and the fluid supply chamber R.
2, and communicate with each other through a through hole 53 and a communication passage 54 (see FIG. 2). Thus, the pressure chamber R3 is filled with the brake fluid at atmospheric pressure. The inside of the wheel cylinder 17 communicating with the pressure chamber R3 via the hydraulic path 26 is also maintained at substantially the atmospheric pressure.

As shown in FIGS. 1, 4 and 5, in this initial state (return state), the opening of the first communication hole 70 of the spool cylinder 34 is closed by the spool valve 35. The first communication hole 70 and the control room R4 are substantially shut off. Therefore, the first
The auxiliary hydraulic pressure source 14 communicating with the communication hole 70 via the circumferential groove 73 and the hydraulic pressure passage 28 is isolated from the control room R4. Further, the opening of the second communication hole 71 of the spool cylinder 34 is not closed by the spool valve 35, and the hollow portion of the spool cylinder 34 and the control chamber R4 communicate with the second and third communication holes 71, It communicates via 72. Therefore, the brake fluid reservoir 13 and the control chamber R4 communicate with each other through the fluid pressure passage 24, the circumferential groove 69, the through hole 68, and the second and third communication holes 71 and 72. As a result, the control chamber R4, the reaction chamber R4 communicating with the control chamber R4 through the circumferential groove 76, the hydraulic pressure path 27, the circumferential groove 30, and the through hole 88 are formed.
5, the reaction force chamber R5 and the through-hole 87, the circumferential groove 30, the hydraulic path 2
2. The power chamber R1 communicating with the peripheral groove 29 and the clearance C1 (see FIG. 2) is also filled with the brake fluid at substantially atmospheric pressure. The power room R1 (control room R4) and the clearance C1, the circumferential groove 29 and the hydraulic passage 25
The inside of the wheel cylinder 18 which is communicated with the air pressure is also maintained at substantially the atmospheric pressure.

On the other hand, as shown in FIGS. 2, 3, and 6 to 8, when the brake pedal 10 is operated from the initial state (return state) of the brake pedal 10, the push pedal 11 is used. The master piston 31 (the first and second pistons 41 and 42, the transmission member 46, and the contact member 47) moves forward, and the second piston 42 is pressed by the valve body 32. At this time, the opening of the communication passage 54 is closed by the elastic body of the valve body 32, and the pressure chamber R
3 (hollow portion of the valve body support portion 52) and the communication passage 54 are shut off. Therefore, the inside of the pressure chamber R3 is provided with the liquid supply chamber R2.
(The brake fluid reservoir 13) and is closed. For this reason, the brake fluid of the pressure generated in the pressure chamber R3 according to the stroke amount of the brake pedal 10 (master piston 31) is transmitted to the pressure chamber R3 and the hydraulic pressure path 2
6 and is supplied into a wheel cylinder 17 which is in communication with the wheel cylinder 17.

Further, as the master piston 31 advances, the control piston 33 integrally advances through a spring 63. And this control piston 33
The spool valve 35 fitted to the body also advances integrally. When the control piston 33 (spool valve 35) moves forward, the opening of the second communication hole 71 is closed by the spool valve 35 (second bank 77). The control chamber R4 communicating through the three communication holes 72 is provided with the brake fluid reservoir 13
Be cut off from. Further, the first communication hole 70 and the control chamber R4 are formed between a communication passage formed between the first communication hole 70 and the first peripheral groove 77, between the peripheral groove 66 and the first peripheral groove 77. And a communication path formed between the circumferential groove 66 and the first bank 79. Therefore, the auxiliary hydraulic pressure source 1
4 and the control chamber R4 communicate with each other via the hydraulic path 28, the peripheral groove 73, the first communication hole 70, the peripheral groove 66, the first peripheral groove 77, and the like. When switching to this communication state, the second bank 80
Is formed with an inclined surface 80a.
As described above, the brake fluid smoothly flows into the first circumferential groove 77 side without causing cavitation, for example, in the high-pressure (power hydraulic pressure) brake fluid from the fourth (first communication hole 70). It is. The high-pressure brake fluid that has flowed into the first circumferential groove 77 is again narrowed in the communication path formed between the circumferential groove 66 and the first bank 79, and then flows into the second circumferential groove 77. It flows into the 78 side. As described above, the high-pressure brake fluid from the auxiliary hydraulic pressure source 14 is supplied to the control chamber R4. Thereby, the reaction chamber R4 communicates with the peripheral groove 76, the hydraulic path 27, the peripheral groove 30, and the through-hole 88 through the reaction force chamber R5, the reaction chamber R5 and the through-hole 87, the peripheral groove 30, The auxiliary hydraulic pressure source 14 is also provided in the power chamber R1 communicating with the hydraulic pressure path 22, the circumferential groove 29 and the clearance C1.
High-pressure brake fluid is supplied. The advance of the master piston 31 is assisted by the pressure acting on the boundary surface between the disk portion 43 and the cylindrical portion 44 of the first piston 41 in the power chamber R1, and the brake fluid in the pressure chamber R3 is further reduced. It is compressed and supplied to the wheel cylinder 17 via the hydraulic path 26. The brake fluid in the power chamber R1 (control chamber R4) is supplied into the wheel cylinder 18 via the clearance C1, the circumferential groove 29, and the hydraulic path 25.

Here, if the force applied to the control piston 33 based on the hydraulic pressure in the control chamber R4 is greater than the force applied to the control piston 33 based on the hydraulic pressure in the pressure chamber R3,
The control piston 33 moves rearward to move the second communication hole 7.
Reference numeral 1 denotes a control chamber R4 which opens into a hollow portion of the spool cylinder 34 and communicates with the second communication hole 71 and the third communication hole 72.
Is connected to the brake fluid reservoir 13 and communicates with the control room R4.
The inside is decompressed.

On the other hand, if the force applied to the control piston 33 based on the hydraulic pressure in the control chamber R4 is smaller than the force applied to the control piston 33 based on the hydraulic pressure in the pressure chamber R3, the control piston 33 becomes By moving forward, the second communication hole 71
Is closed by the spool valve 35, and the control chamber R4 is replaced with the hydraulic pressure path 28, the circumferential groove 73, and the first communication hole 7.
The pressure in the control chamber R4 is increased by communicating with the auxiliary hydraulic pressure source 14 via the peripheral groove 66, the first peripheral groove 77, and the like.

By repeating the movement of the control piston 33, the force applied to the control piston 33 based on the hydraulic pressure in the control chamber R4 and the force applied to the control piston 33 based on the hydraulic pressure in the pressure chamber R3. Is controlled so as to match. When the pressure in the control chamber R4 (reaction chamber R5) is smaller than a predetermined pressure, a first-stage brake fluid pressure characteristic corresponding to the stroke amount of the brake pedal 10 is obtained. At this time, the pressure chamber R3 and the control chamber R
A predetermined pressure ratio is maintained between four.

When the pressure in the control chamber R4 (reaction chamber R5) exceeds a predetermined pressure, the reaction force disc 39 is pressed by the liquid pressure as shown in FIG. It elastically deforms to swell inside. At this time, the bulging portion of the reaction force disc 39 is
, And the reaction force rod 38 is pushed rearward on the plunger 36 side. When the rear end of the reaction force rod 38 is pressed by the contact portion 36a of the plunger 36, the spool valve 35 is pushed back. As a result, the second communication hole 71 opens in the hollow portion of the spool cylinder 34, and the control chamber R4 that communicates with the second communication hole 71 and the third communication hole 72 communicates with the brake fluid reservoir 13. The pressure in the control room R4 is reduced. Then, a second-stage brake fluid pressure characteristic is obtained in which the pressure increase gradient with respect to the stroke amount of the brake pedal 10 is gentler than the first-stage brake fluid pressure characteristic. At this time, a predetermined pressure ratio is maintained between the pressure chamber R3 and the control chamber R4.

The first and second brake fluid pressure characteristics according to the stroke amount of the brake pedal 10 provide a favorable pedal operation feeling. As described in detail above, according to the present embodiment, the following effects can be obtained.

(1) In the present embodiment, since the second bank 80 is formed gently via the inclined surface 80a,
The high-pressure (power hydraulic) brake fluid from the auxiliary hydraulic pressure source 14 (first communication hole 70) can be smoothly introduced into the first circumferential groove 77 without causing cavitation, for example. it can. For this reason, the auxiliary hydraulic pressure source 14
The high-pressure brake fluid from the (first communication hole 70)
4 can be suppressed from generating noise and vibration.

(2) In this embodiment, the spool valve 3
The first and second peripheral grooves 77 and 78 provided on the outer peripheral surface of the outer peripheral surface of No. 5 form a concave portion. Therefore, the flow path formed between the spool cylinder 34 and the first and second circumferential grooves 77 and 78 is maximized, and the high-pressure brake fluid can be quickly supplied to the control chamber R4.

The first and second circumferential grooves 77, 78
Can be easily processed by, for example, a lathe operation. (3) In the present embodiment, the high-pressure brake fluid that has flowed into the first circumferential groove 77 side is again narrowed in the communication path formed between the circumferential groove 66 and the first bank 79 after the flow path is narrowed. , Second
It flows into the peripheral groove 78 (control room R4). Therefore, the pressure difference between the brake fluid flowing into the control room R4 and the brake fluid can be reduced, and the generation of noise and vibration can be further suppressed.

(4) In the present embodiment, the steps formed at the rear and front of the first bank 79 are respectively
a, 79b, the high-pressure brake fluid flowing into the first circumferential groove 77 is smoothly squeezed in the communication passage formed between the circumferential groove 66 and the first bank 79, and further narrowed. The applied brake fluid can flow smoothly into the second circumferential groove 78 side (control room R4).

(5) Generally, the hydraulic brake device is mounted immediately in front of the brake pedal 10 arranged in the driver's seat. In the present embodiment, since the generation of noise and vibration due to cavitation and the like of the brake fluid can be suppressed, the generation of unpleasant noise and the like transmitted to the driver can also be reduced.

The embodiment of the present invention is not limited to the above embodiment, but may be modified as follows. In the above-described embodiment, the inclined surfaces 79 a and 7 are respectively provided on both the step portions formed at the rear portion and the front portion of the first bank 79.
Although 9b is formed, it may be formed only on one of the two step portions formed on the rear portion and the front portion. Further, such an inclined surface is not necessarily required.

In the above embodiment, the first and second
Although the concave portions are formed by the peripheral grooves 77 and 78, for example, the concave portions may extend in the axial direction along the outer peripheral surface. In the above-described embodiment, the inclined surface 80a that is continuous in a substantially straight cross section is formed in the second bank 80. However, for example, the inclined surface that is continuous in a curved surface having a predetermined curvature or a continuous combination thereof is used. It may be an inclined surface.

In the above embodiment, the shape of the communication hole (first communication hole 70) formed in the spool cylinder 34 is merely an example, and other shapes may be used. The point is that high-pressure brake fluid from the auxiliary hydraulic pressure source 14 may be introduced into the hollow portion of the spool cylinder 34.

In the above-described embodiment, the present invention is applied to the hydraulic brake device. However, the present invention may be applied to other devices having a similar hydraulic circuit.

[0068]

As described above in detail, according to the first aspect of the present invention, it is possible to suppress noise and vibration generated when a high-pressure fluid from a high-pressure source is supplied to a pressure forming chamber. it can.

According to the second aspect of the present invention, the flow path formed between the cylindrical body and the concave portion is maximized, and the high-pressure fluid can be quickly supplied to the pressure forming chamber. Further, such a concave portion can be easily processed by a lathe operation.

According to the third aspect of the invention, it is possible to reduce the pressure difference between the high pressure fluid flowing into the pressure forming chamber and the noise and vibration. According to the fourth aspect of the present invention, the high-pressure fluid introduced into the flow path formed between the cylindrical body and the concave portion is smoothly throttled, or the throttled high-pressure fluid is smoothly flowed into the pressure forming chamber. Can be.

According to the fifth aspect of the present invention, since the generation of noise and vibration due to the cavitation of the high-pressure fluid is suppressed, it is possible to reduce the generation of unpleasant noise transmitted to the driver. .

[Brief description of the drawings]

FIG. 1 is a sectional view showing an embodiment of a hydraulic brake device to which the present invention is applied.

FIG. 2 is an exemplary sectional view showing an operation mode of the embodiment;

FIG. 3 is an exemplary sectional view showing an operation mode of the embodiment;

FIG. 4 is an exemplary sectional view showing a main part of the embodiment;

FIG. 5 is an enlarged sectional view showing a main part of the embodiment.

FIG. 6 is an exemplary sectional view showing a main part of the embodiment;

FIG. 7 is an enlarged cross-sectional view showing a main part of the embodiment.

FIG. 8 is an exemplary sectional view showing an operation mode of the embodiment;

FIG. 9 is an exemplary sectional view showing an operation mode of the embodiment;

FIG. 10 is a sectional view showing a conventional high-pressure fluid supply device.

FIG. 11 is a sectional view showing an operation mode of the device.

[Explanation of symbols]

 R4 Control chamber as pressure forming chamber 14 Auxiliary hydraulic pressure source as high pressure source 34 Spool cylinder as cylinder 35 Spool valve as shaft 70 First communication hole as communication hole 77 First peripheral groove forming recess 78 second peripheral groove constituting a concave portion 79 first bank 79a, 79b, 80a as a projecting portion inclined surface

Claims (5)

[Claims] 1. A cylinder provided with a communication hole for introducing a high-pressure fluid from a high-pressure source into a hollow portion, and a pressure formed between the cylinder and the cylinder body slidably supported by the hollow portion of the cylinder. A shaft formed on an outer peripheral surface of a recess forming a flow path communicating with the chamber, the cylinder and the shaft are relatively moved to open the communication hole in the recess, and a A high-pressure fluid supply device for supplying a high-pressure fluid to a pressure forming chamber, wherein the step formed on the outer peripheral surface of the shaft by the concave portion is formed smoothly through an inclined surface. Feeding device. 2. The high-pressure fluid supply device according to claim 1, wherein the recess is provided around the shaft. 3. The high-pressure fluid supply device according to claim 1, wherein the recess is provided on the shaft side to narrow a flow path communicating with a pressure forming chamber formed between the recess and the cylindrical body. A high-pressure fluid supply device, wherein a projecting projection is formed. 4. The high-pressure fluid supply device according to claim 3, wherein the step formed on at least one of the upstream side and the downstream side of the protruding portion is formed gently via an inclined surface. A high-pressure fluid supply device. 5. A hydraulic brake device for a vehicle, comprising the high-pressure fluid supply device according to claim 1.